Printing telegraph apparatus



June 20, 1944. A. H. REIBER PRINTING TELEGRAPH APPARATUS Original FiledMay 4, 1936 10 Sheets-Sheet 1 FIG. I

INVENTOR ALBERT H. REIBER ATTORNE June 20, 1944. A. H. REIBER 2,351,784

PRINTING TELEGRAPH APPARATUS Original Filed May 4, 1936 110 Sheets-Sheet2 INVENTOR ALEERT H. REIBER "A'r'ro EY June 20, 1944. A. H. REIBER2,351,784

PRINTING TELEGRAPH APPARATUS Original Filed May 4, 1956 10 Sheets-SheetI5 TO MOTOR CONTROL MECHANISM FIGv 23 I INVENTOR TO 'TAPE ALBERT H.REIBER TRANSMITTER 466 ;467 J66 ATTORNE June 20, 1944. REIBER PRINTINGTELEGRAPH KPPARATUS 4 Original Filed May 4, 1936 10 Sheets-Sheet 4 FIG 4ZZLEFIIIIIIIIHHI QEEM E II.

FIG. 22

INVENTOR ALBERT H. REIBER my ATToRN A. H. REIBER June 20, 1944.

PRINTING TELEGRAPH APPARATUS Original FiledMay 4, 1936 10 Sheets-Sheet 5INVENTOR ALBERT H. REIBER FIG. 5

.' ATTOR EY June 20, 1944. A. H. REIBER PRINTING TELEGRAPH APPARATUSOfiginal Filed May 4, 1936 10 Sheets-Sheet 6 INVENTOR ALBERT H. REIBERJune 20, 1944. A. H. REIBER PRINTING TELEGRAPH APPARATUS Original FiledMay 4, 1936 10 Sheets-Sheet 7 I6. IO

- INVENTOR ALBERT H. REIBER 'ATI'ORNE June 20, 1 944. A. H. REIBER2,351,784

PRINTING TELEGRAPH APPARATUS Original Filed May 4, 1936 10 Sheets-Sheet8 FIG. l2

Big/3 362 v 373 372 387 386 y 377 an 369 376 2 INVENTOR 388 ALBERT H.REIBER ATTORNE June 20, 1944. RElBER PRINTING TELEGRAPH APPARATUSOriginal Filed May 4, 1936 10 Sheets-Sheet 9 ATTORNEY June 20, 1944. A.H. REIBER PRINTING TELEGRAPH APPARATUS Original Filed May 4, 1936 10Sheets-Sheet 10 mu llllmm lnulllmjlllll' I. 8M'fimpm FIG.2|

INVENTOR.

ALBERT H. REIBER Patented June 20, 1944 PRINTING TELEGRAPH APPARATUSAlbert II. Reiber, Evanaton, Iil., minor to Teletype Corporation,Chicago, Ill., a corporation of Delaware Original application. May 4,1936, Serial No. 77,796. Divided and this application June 14, 1941,Serial No. 398,074

6 Claims. (Cl. 197-89) The principal object of the invention is to endowa type wheel printer with many of the advantageous features of a typebar printer while retaining the simplicity of constructioncharacteristic of type wheel printers.

. A further object is to provide a, type wheel printer having theprincipal operating characteristics of certain commercially used typebar printers so as to be capable of being operated over the sametelegraph circuits and in interconnection with the commercially usedtype bar printers to record the same message in line for linearrangement and perform the same functions as the type bar printer.

The invention also features function mechanism in which the performanceof any function may be blocked by an element or elements associated withthe case shift mechanism of the printer. Thus, two functions, or acharacter selection and a function may be associated with one codecombination. Under these circumstances, selection between the twofunctions, or between the character and the function, is determined byselective case shift conditioning preceding the function selection.

Briefly, the principal elements of the receiving apparatus are aselecting mechanism including a single magnet selector and a code discselector, power driven operating cams controlled from the selectingmechanism, a type wheel and means for stopping it in accordance with theoperation of the code disc selector. cam operated means for effectingprinting from the type wheel, cam controlled and operated mechanisms forperforming the necessary stunts or functions of the printer, mechanismfor feeding an inked ribbon between the type wheel and a printing platenincluding means for controlling'the direction of feeding of the ribbon.and a movable carriage which carries the paper upon which printing is tobe effected.

The single magnet selector operates in accordance with signal impulsesreceived sequentially to position settable elements correspondingly.Power operated transfer mechanism then operates through the elementsthus set to transfer simultaneously all of the conditions established bythe received signal impulses to a code disc selector which has aplurality of stop elements, any one of which, upon selection, isprojected into the 'path of an arm on a type wheel shaft, to which aconstant torque is applied, to stop the type wheel in a positioncorresponding to the received signal combination. The single magnetselector mechanism controls the operation of a set of operating cams,one of which operates the transfer mechanism to effect the setting ofthe code discs, another of which operates a printing bail and inaddition, under certain selective conditions, performs certainnon-printing functions and conditions other non-printing functions forperformance, and the third and final cam of which operates the spacingmechanism and performs those functions that are conditioned but notperformed by the printing bail. Spacing from one character to anotherand between words i accomplished through a pawl and ratchet, the latterof which is connected to a pinion meshing with a rack included in theplaten carriage. The spacing operation tends to be performed withinvariable regularity but is, under certain circumstances, suppressed,as for example, during the performance of functions which, ifaccompanied by spacing, might result in the introduction of undesirablespaces in the printing of letter combinations. Those functions which areperformed by operation of the spacing cam are the functions which it isdesirable to perform slowly, in order to obviate attempted violentmovement of relatively massive elements. Those functions that areperformed by the print bail operating cam are functions involving themovement of relatively light elements, the inertia of which iscomparatively low so that they may be operated with relatively greatrapidity, as the printing bail operating cam is arranged to perform anoperation in a very brief interval. In the case of certain functions, ayielding connection is provided between a function conditioning leverand an associated lever, and the latter lever may be blocked by anydesired means and in particular by the case shift mechanism of theprinter, so that the function conditioning operation may be dissipatedin the yieldable connection and the performance of a function may bemade dependent not only upon a particular code combination associatedwith that function, but also upon the predetermined condition of thecase shift mechanism as determined by a previously received differentcode combination.

The particular type wheel mechanism disclosed herein is fully describedand claimed in a copending application of Howard L. Krum et al.,

- carries a plurality of transmitting earns 22.

Serial No. 77,794. filed on May 4. 1936, which matured on November 21,1939, into Patent No. 2,180.360.

Fora more complete understanding of the invention, reference may be hadto the following detailed description. taken in conjunction with theaccompanying drawings in which Fig. 1 is a perspective view of thecombined transmitting and receiving apparatus in accordance with theinvention;

Fig. 2 is a front elevational view of the receiving and printingmechanism;

Fig. 3 is a side elevation of the transmitting and receiving mechanism;

Fig. 4 is a vertical sectional view through the receiving and printingmechanism;

Fig. 5 is a top plan view of the transmitting and receiving mechanism;

Fig. 6 is a detailed plan view of the selecting mechanism and portionsof the carriage mechanism;

Figs. 7 and 8 are respectively, elevational and plan views of the caseshift mechanism;

Fig. 9 is a horizontal sectional view showing the spacing and functionperforming mechanisms;

Fig. 10 is a horizontal sectional view showing details of the spacingmechanism;

Fig. 11 is a horizontal sectional view showing details of the transfermechanism;

Fig. 12 is an exploded view in perspective of the function selecting andperforming mechanisms;

Fig. 13 is a perspective view of the ribbon feed mechanism;

Figs. 14 and 15 are plan views of the ribbon feed mechanism showingdifferent conditions of operation;

Fig. 16 is a vertical sectional view through the ribbon feed mechanism;

Fig. 17 is a perspective view of the platen carriage showingparticularly paper holding .and guiding means;

Fig. 18 is a perspective view of a removable paper roll holder shown inbroken lines in Fig. 17;

Fig. 19 is a perspective view of a paper guiding plate;

Fig. 20 is a vertical sectional view through the platen carriage showingthe manner of mounting the plate shown in Fig. 19 upon the carriage;

Fig. 21 is a vertical sectional view showing the line feeding mechanism;

Fig. 22 is an elevational view of a modified print hammer operatingmechanism; and

Fig. 23 is a schematic wiring diagram.

Keyboard transmitter Referring now to the drawings and particularly toFigs. 1 and 5, the reference numeral I 5 indicates generally a keyboardtransmitter mechanism which may be of any desired form such as the onedisclosed in U. S. Patent 1,595,472, granted August 10, 1926 to HowardL. Krum. The keyboard transmitter l5 includes a base casting I 6 whichcarries a plurality of character selecting key levers IS. The key leversoperate upon a set of permutation bars (not shown) to controltransmitting apparatus indicated generally by the reference numeral IS.The transmitting apparatus includes a cam shaft 2| which A contactcontrolling bell crank lever 23 is associated with each of thetransmitting cams 22. One end of each of the bell crank levers 23 isdisposed in engagement with one spring of 'a supported on the framemember 36.

pair of transmitting contact springs 24 (Fig. 1) and the other end isaligned with a lever 26 which is controlled by the permutation bars (notshown). In their idle positions, the transmitting cams 22 maintain thebell crank levers 23 in a position such that all but one of the pairs oftransmitting contacts are open, the excepted contact pair being closedfor the application of a stop pulse to the line. Upon the operation of akey lever l8, the permutation bars and therefore the levers 26 whichthey control are set permutatively, whereby certain of the bell cranklevers 23 are blocked so that they cannot rotate and others are freed sothat they may rotate to allow closing of the associated transmittingcontacts 24 when permitted to do so by their associated transmittingcams 22. The transmitting cams are so arranged upon the shaft 2| thatthey release the several transmitting contact bell crank levers 23successively for rotation and thus the transmitting contactscorresponding to the particular permutation code established by theoperated key lever are closed successively. A locking bail 28 has a camfollower 29 which rides on a cam 3| carried by cam shaft 2|. Bail 28drops into blocking relation to the levers 26 after they are set by thepermutation bars and prevents disturbance of an established codecombination during the transmission of the corresponding code impulses.Power for driving the transmitting cam shaft 2| is communicated througha spring loaded clutch 32 from a gear 33 which is driven throughsuitable intermediate gearing 35 from a gear 4| (Figs. 1 and 2).

The base casting l6 removably supports the foundation for a receivingprinter comprising a vertically extending frame casting 36 and a framecasting 31 secured to the casting 36. The frame casting 36 extends fromfront to rear of the base casting l6 and the casting 3'! extendstransversely thereof. The-frame casting 36 has secured thereto bearingblocks 38 which rotatably support a shaft 39. Shaft 39 has securedthereto a gear 4| (Figs. 1 and 2) which is driven by a spiral gear 42(Fig. 4) which is mounted on the rotor shaft of motor 34 and constitutesthe main driving gear of the receiving printer as well as of thetransmitting mechanism. The shaft 39 actuates the selector mechanism ofthe receiving printer and also the operation performing cams.

The driving gear 42 (Fig. 4) also meshes with a gear 43 which is mountedon a shaft 44 and is operatively connected thereto through africtionclutch 46. Shaft 44 is journalled in a code disc selector mechanismindicated generally by the reference numeral 41 (Fig. 3) which isremovably Selecting mechanism :At the top of frame member 36 there ismounted a single magnet selector mechanism which is generally similar tothe selector disclosed in U. S. Patent 1,937,376, granted November 28,1933 to Walter J. Zenner. The selector mechanism (Fig. 6) comprises aset of selector elements in the form of thin, fiat fingers 5| arrangedin superposed relation between guide plates 52. The selector fingers 5|equal in number the signalling elements in the code on which thereceiving printer operates. Thus, if a five-unit code is employed, therewill be five of the selector fingers 5|, whereas a six-unit code willrequire six selector fingers. The guide plates 52 are mounted on studs53 secured to the selector mounting plate 54 and are spaced by washers(not shown). The

circular left ends 88 of selector fingers ll engage correspondingsockets of thin, fiat bell crank levers I1 pivoted on a common shaft 88.Individual springs 68 bias .the bell cranks 81 in their clockwisedirection whereby the selector fingers II are urged rightwardly. Thepointed ends ll of bell crank levers 81 are thus maintained in contact'with a cam barrel 8! which is mounted on [shaft 88 and is driventhereby through friction discs, indicated at 88 (Fig. 4).

Cam barrel 8! is provided with a, helically arranged'series of camprojections 84 (Fig. 8), one for each of the bell cranks 61, whichrotate the bell cranks 81 in succession and thus draw the selectorfingers 8| leftwardly successively as the cam barrel 8! is rotated. Inaddition to the iongitudinal movement, the selector fingers have alaterally swinging movement between a pair of studs 86.

The setting of any selector finger 8| either to its clockwise orcounterclockwise position is determined by the electromagnet 61 which ismounted on the mounting plate 64 and which is provided with armature 68fixed to a flutter lever 88 which is pivoted at 1| to a frame carried bythe supporting plate 64. Mounted on a pivot 12 ad- Jacent to and incooperative relation with the flutter lever 68 is a selector lever 18.Lever 18 terminates in a T-shaped portion 14 having downwardly extendingarms 16 (Fig. 1) which constitute abutments which cooperate with arms 11(Fig. 6) on the left ends of the selector fingers Ill and act toposition the latter in extreme clockwise or extreme counterclockwisepositions. The

several fingers act through a corresponding number of levers 18 arrangedbetween the guide plates 52 and pivotally mounted on a stud 18 toposition a set of transfer bell crank levers 8|, pivoted at 85, whichhave disc portions 82 engaging sockets in levers 18.

A previously stated, each selector finger 8| is shifted clockwise orcounterclockwise by having one or the other' of its arms 11 drawnagainst one or the other of the abutments 16 of the T- shaped portion 14of selector lever 13. The selector lever 13 is connected by a spring 83to an arm 84 of the flutter lever 68 and the minimum distance betweenthe levers 68 and 13 is determined by an abutment screw 86., The flutterlever 68 has a portion which follows a flutter cam 81 (Figs. 2 and 4)included in the cam barrel assembly 62.

As the signal impulses are received over the telegraph line, theelectromagnet 61 is energized and deenergized depending upon the natureof such impulses. During the reception of a set of impulses constitutinga signal, the cam barrel 62 is rotated, flutter lever 68 follows fluttercam 81, and armature 68 is moved cyclically into engagement with itspole face. If the armature 88 is then held due to the presence of anenergizing impulse through the winding of its electroma gnet connectedin the line. the flutter lever 68 will be prevented from following thecontour of the flutter cam 81. The abutment screw 86 and spring 83 causethe selector lever 13 to follow the motions of the flutter lever 68 sothat when the levers are moved counterclockwise, one of the abutmenrs 16of selector lever 13 is moved into alignment with one set of arms 11 ofthe selector fingers 5| and when the levers are rotated to their extremeclockwise positions. the other abutment 16 is moved into alignment withthe other set of arms 11. The several earns 64 on the cam barrel 8! areso positioned with respect to the flutter cam 81 that the selectorfingers 5| are drawn leftwardly in synchronism with the signallingimpulses received by the selector magnet 81 so that a selector finger 8|will be moved from a position corresponding to a spacing signal to aposition corresponding to a marking signal only if the armature 88,after being rotated into engagement with its pole face by flutter cam81, is held by the electromagnet as the selector finger 4| is drawnleftwardly by its associated bell crank lever 81 and will not be soshifted as a result of mere movement of the armature 88 as the flutterlever 88 follows a high portion of flutter cam 81. A cam operated locklever 88 locks and releases selector lever 13 at proper intervals undercontrol of a cam 88 on the cam barrel 82.

The transfer bell crank levers 8| are connected by socket connections tothe code discs of a code disc selector -mechanism which, as previouslymentioned, is designated generally by the reference numeral 41. Theselector mechanism 41 includes code discs 8| equal in number to thenumber of selector fingers 5|, and each of the discs is supported so asto be rotatably responsive to the transfer bell crank lever 8| to whichit is articulated. I The discs 8| have their edges notched permutativelyso that for each permutative setting of the discs a single completealignment of notches of the several discs will be efi'ected.

The code disc selector mechanism 41 has plates 82 and 83 (Fig. 4)disposed respectively above and below the code discs 8| and a plate 84disposed below and at some distance from the plat 88. The three plates82, 83, and 84 have radially arranged slots equi-distantly spaced, theslots corresponding in number and positions to the permutative alignmentof the notches in the code discs 8|. A selectable stop pin 88 isdisposed in each vertical alignment of slots in the discs 82, 88, and 84and each pin has a portion extending below the disc 84, which portion iseyelet-shaped. and a straight portion extending above the disc 82. Agarter spring 81 surrounds all of the stop pins 86 and retains themproperly seated in the disc 84.

Each of the pins 86 carries anti-friction rolls 85 (Figs. 4 and 6) equalin number to and in alignment with the code discs 8|. With anypermutative disposition of the code discs 8| an alignment of notcheswill be presented opposite the anti-friction rolls carried by one of thestop pins 86. The stop pin opposite which the notches are aligned pivotsabout the inner limit of the slot in the plate 84 so that its upper endmoves toward the type wheel shaft 44 in a direction radially of saidshaft as the anti-friction rolls 85 become seated in the alignment ofnotches in the code discs. Only one of the stop pins 86 can be selectedat a particular time due to the fact that there cannot be two alignmentsof code disc notches simultaneously.

The type wheel shaft 44 carries in fixed relation thereto a stop arm 88,the outer end of which clears unselected stop pins 86 but is blocked bya selected stop pin and is prevented from further rotation until theselected pin has been cammed outwardly by one or more of the code discsdue to a change in their permutative arrangement. A leaf spring 88 (Fig.6) carried by the stop arm 88 precedes the stop arm 88 as the shaft 44rotates and the end of the lead spring 88 passes over the top of anystop pin 86 that is selected and drops ahead of the pin when the arm 88is stopped, thereby confining the pin between the arm 88 and the leafspring 88 and preventing the stop arm from bouncing away from the stoppin 96 by which it has been arrested. The shaft 44 carries a type wheelwhich Is designated generally by the reference numeral I The selectiveoperation of the stop pins 96 determines stop positions of the typewheel.

Transfer mechanism The shifting of the code discs 9| to establishsuccessive selections of the stop pins 96 is effected through the mediumof a power actuated transfer bail I02 (Figs. 1, 2, 3, 6, and 11). Theball I02 i pivoted on a shaft I03 and has a lever I04 adjustablyconnected thereto by screw I05. The lever I04 carries a cam followerroller I08 which rides against a cam I01. The ball I02 has at its upperend a vertically extending arm I08 to which is secured by bolts I09 aU-shaped extension III (Fig. 6). The arm I08 and the opposite sideportion of the extension III are provided with rectangular apertureswhich receive U-shaped springs I I2. One arm of each of the springs 2extends through the aperture in the arm I08 of transfer bail I 02 andterminates in alignment with one of the bell crank levers 51. The otherarm of each of the springs I|2 terminates in the aperture in the arm I08and is confined there by that arm of the U- shaped extension III whichis secured by the screw I09 and which partially covers the aperture inarm I08, The springs II2 are under tension in the aperture in thevertical arm I08.

The springs II2 serve as individual yielding operating connectionsbetween the transfer ball I02 and the several bell crank levers 51. Whenthe transfer bail I02 is rocked in a clockwise direction by cam I01, theends of the springs |I2 engage the bell crank levers 51 and rock themclockwise and the bell crank levers in turn shift the selector fingersrightwardly. The selector fingers 5| rock the levers 18 clockwise orcounterclockwise, depending upon the positions into which the fingers 5|have been moved through the action of the selector magnet 61, selectorlever 13, and bell crank 51. As previously described, shifting of thelevers 18 causes corresponding shifting of the transfer bell cranklevers 8| which are articulated to the code discs 9| so that permutativearrangements of the code discs in accordance with signals received bythe selector magnet 61 are set up when the transfer bail I02 is actuatedin a clockwise direction. Springs 59 bias the bell crank levers 51 inclockwise direction, as previously described, and while the springs maybe of sufi'icient tension to shift selector fingers 5|, the levers 18,transfer levers 8|, and code discs 9|, it has been found desirable notto rely on the springs to effect the transfer of selections to the codediscs, and to this end a locking bar has been provided to prevent thesprings from effecting such transfer at all times except when thetransfer bail is to be operated.

The transfer bail is provided with an extension arm I I3 whichterminates in a knife-edge H4. The levers 18 are provided withextensions II6 which terminate beyond the position occupied by theknife-edge II 4 when the transfer bail I02 is in its extremecounterclockwise position. The knife-edge 4 thus serves when in lookingposition to restrain the levers 18 from being moved by the springs 59.Since the extension arm 3 is carried by the transfer bail I02, 'it iswithdrawn to a position which clears the ends I I6 of the levers 18 whenthe transfer bail is rocked in a clockwise direction and at this timethe code discs are shifted by the combined action of the transfer bailI02 operating through springs H2 and the springs 59. Arm II3 returns tolocking position when the transfer bail I02 is restored to its normal orunoperated position.

Type wheel The type wheel shaft 44 has a reduced portion I2I at theupper end thereof which provides a shoulder I22 (Fig. 4). A hub I23 isjournalled on the reduced portion I2I of shaft 44 and is slidablethereon. At its upper end the hub I23 car ries a disc I24 to which issecured an annular type wheel frame I26. The frame I26 has slots inradial arrangement equally spaced therearound, and in each of the slotsupper and lower type pallets I21 are slidably disposed. The type palletsI21 are arranged in upper and lower annular rows, one row of which maycarry any desired group of characters such as letters and the other ofwhich may carry other characters such as figures and punctuation marks.The type pallets comprise type faces I28 to which are secured thinshanks I29 which extend inwardly and radially of the type Wheelstructure within the radial slots thereof. The shanks of each annularrow of type pallets are notched to receive a garter spring I 3| whichbiases all of the type pallets of an annular row to their innermostpositions with the type face I28 disposed about the periphery of theslotted frame I26. An annular ring I 32 is fioatingly disposed in thenotches in both annular rows of type pallets and prevents the typepallets from accidental displacement from the type wheel structure dueto centrifugal force in the event that one of the garter springs .I3Ishould break. At one portion of its periphery,

the type wheel structure has no type pallets and at that point the discI24 and frame I26 are provided with recesses in which is disposed aperpendicular portion I33 of a type wheel driving arm I34 which isadjustably secured by screws I30 to an arm I35 which is carried by thetype wheel shaft 44 at the top thereof in fixed relation to the shaft tobe driven thereby. The adjustability between the arms I34 and I35 isangular.

The type wheel structure is slidable longitudinally of the type Wheelshaft to bring either of the two rows of type pallets into printingalignment with the printing platen, the shifting of the structure beingaccomplished by a sliding movement of the hub I 23 with respect to thetype wheel shaft 44 produced by mechanism to be described hereinafter.As the type wheel is shifted, the recesses in which the perpendicularportion I33 of driving arm I34 i disposed slide upon the portion I33 anddriving relation between the type wheel shaft and the type wheel ismaintained. A printing hammer I36 is pivotally mounted on screws I31threaded into the stationary bracket I25 (Fig. 3) and has its head inalignment with the printing position so that it is disposed behind theshank of the type pallet of either of the annular rows of type pallets,depending upon whether the type wheel is in its upper or lower position.The printing hammer I36 has integral therewith a bail portion 9 at theopposite end of which is integrally formed a lever arm II 1 (Figs. 1 and3) which carries an impact receiving member I38. A limit screw II8limits the operative movement of lever arm H1. The lever arm 1 isactuated by a striker member to be described later. The operativemovement of the print hammer I36 is a sudden clockwise rotation asviewed in Fig. 4, whereby thetype pallet which is aligned with the printhammer at the moment is driven outwardly and radially of the type wheelstructure into engagement with the printing platen I 89. A stop bar Imounted on top of the bracket I24 projects into the path of the hammerI84 and limits the movement thereof.

Carriage mechanism The printing platen I39 is rotatably mounted in endplates I40 of a reciprocating carriage I (Fig. 1). The carriage I issupported in adjustable rails I42 at the top of the main frame 1 I42 andprovide free movement of the carriage with respect to its supportingrails. The rotatable platen is provided with a feed ratchet I44 (Fig. 2)with which there cooperates a feed pawl I I41 (Fig. 21).

The platen feeding pawl is articulated to a lever I49 (Fig. 21) that isilxed to a rock shaft I50. The rock shaft I50 is rotatably journalled inthe carriage HI and has fixed thereto at a point substantially midwaybetween the ends of the carriage I an operating lever I60. The leverI49, rock shaft I50, and operating lever I50 are biased counterclockwiseby a spring I65. Feeding of the ratchet I49 in the direction indicatedby the arrow is effected by clockwise rota-' tion of operating leverI60, by a power actuated bail to be described later, against the tensionof spring I65, which subsequently acts to reciprocate the pawl I41 topick up-the next tooth or teeth for the next line feeding operation. A

' member 91. Anti-friction balls I48 (Fig. 4) are disposed between thecarriage I and the rails lever I10, pivoted on the carriage end plateI40,

provides two abut'ments for deflecting the pawl at different points inits travel to idle or unoperated position to establish single or doubleline spacing. When the lever is in the position shown to pick up onlyone tooth. An adjustable eccentric I15'is mounted on the carriage endplate I40 and is disposed in the path of a camming lug I85 on the pawlI41 for wedging the pawl against the ratchet to prevent over-travel ofthe ratchet and platen. A spring biased jockey roll I90 bears againstthe ratchet I48 and controls the positioning of the platen I39.

The carriage I is moved to its right-hand position by a belt I5I (Fig.2), which has one end connected to a drum I52 which contains a spiralspring by which the drum is urged to rotate in a clockwise direction andwhich has its other end connected to a pin I53 (Figs. 3 and 6) carriedby the carriage MI. The carriage MI is moved leftwardly byspacingmechanism to be described hereinafter against the action of the spiralspring. A lever I56 pivoted at I51 (Fig. 3) has one end articulated tothe plunger rod I58 of a dashpot I59 and has its other end positioned tobe engaged by the carriage I as it travels into its extreme right-handposition by the action of the spiral spring. With this arrangement, thereturn of the carriage to its extreme right-hand position is cushionedby the dashpot I58. Stop screws I54 threadedly engage the carriagesupporting portion I41 of the frame casting 31 at opposite ends of saidportion, and the inner ends screws I44 limit the movement of thecarriage in both directions of travel.

Ribbon mechanism At the top of the printer and adjacent to the typewheel assembly IOI there is provided a ribbon feed mechanism designatedgenerally by the reference numeral I4I (Figs. 1, 2, 3, 4, 5, 13, 14, 15,and 16 for supporting an inked ribbon similar to the ribbons employedintypewriting machines and for feeding the ribbon past the printingposition and between the type pallets and the printing platen. Thereference numeral I82 designates a plate which is the foundation of theentire ribbon feed mechanism and which is in turn supported on theprinter by means of osts I48 so that the complete ribbon feed mechanismis removable as a unit.

The plate I42 carries arcuate ribbon guide band I84 which guides theribbon around the type wheel assembly IN and which is provided with anaperture I96 through which the type pallets may strike against thepaper, upon which characters are to be recorded, with the ink ribboninterposed between the type pallets and the paper whereby a characteris'imprinted upon the paper. Ribbon spool supporting pins. I81 areiournalled in the side arms of the plate I62 and each pin has securedthereto above the plate I92 a disc I98 and at the lower end of the pinbelow the plate I92 a ratchet wheel I89 which may be rotated by means ofa pawl to cause the positive rotation of the pin I41 and disc I99. Eachof the discs I98 carrie a pin "I which engages a ribbon spool I12 tocause the spool to be driven when the ratchet I68 is positively rotatedby its operating pawl.

- generally by the numeral I16. The lever a bracket I45 mounted on thecarriage I M. The

The plate I82 carries a pivot pin I13 on which, below the plate I92, arepivoted two levers, one of which is designated generally by thereference numeral I14, the other of which is designated I14 hasoppositely extended symmetrical arms I11 at the outer ends of which areportions I18 formed perpendicular to the arms I 11 and bifurcated. Thepath of the ink ribbon, as it passes from one spool to another. isthrough the bifurcations in the perpendicular portions I18 of the arms I11. The lever I14 also has an arm I19 extending away from the arms I11on the line of a bisector of the angle between the arms I 11. This arm I19 is widened at its outer end as shown at I8I and an additional arm I82which is pointed at its outer end cooperates with a spring I to serve asa jockey to maintain the lever I14 in either of the two positions towhich it may be shifted. Lever I19 has the general contour of a bellcrank lever, one arm I84 of which has at its outer end shoulders Idisposed in the plane of the ratchet wheels I99 to serve as a retainingpawl for either of the ratchet wheels to prevent the wheel from slippingback as it is advanced by the feed pawl. The arm I94 of the bell cranklever I16 is provided intermediate its ends with an aperture I81 whichis substantially parallelogrammatic and which may be described roughlyas diamond shaped. Manifestly, the lever I18 is limited in movement bythe two ratchet wheels I69. The other arm I98 of the bell crank leverI16 supports one end of the tension spring I89, the other end of whichengages a spring post I9I which is so positioned that as the lever I 16shifts from engagement with one ratchet wheel to engagement with theother, the spring I89 is carried across the pivot pin I19 and serves asan over-center device for the lever I16.

An operating lever I92 for the ribbon feed mechanism is pivoted to plateI62 at I" and carries at its inner end a pivot pin I94 on which ispivotally mounted the ratchet feed pawl indicated generally by thereference numeral I96.

' The feed pawl I96 is U-shaped and both arms the ratchet wheels I69.Intermediate the ratchet engaging portion there is a depending pin 202which extends into the diamond-shaped aperture I81 in the lever I16. Afloating link 299 has one end engaging the upper end of pin 202 and theother end engaged by a tension spring 204 which is connected to theplate I62. The spring 204 and link 208 serve as an over-center devicefor the feed pawl I96 and bias the operating arm I92, by-which thestepping pawl is carried, to the unoperated position. A power actuatedlever 206 carrying a link 205 which engages the ribbon feed operatinglever I92 cyclically operates the lever by rotating it clockwise inopposition to the tension of spring 204. Lever 206 is pivotally mountedat 208 (Fig. 1) and is actuated by lever arm 249, which, as will appearsubsequently, is operated by a cam. Leaf springs 201 frictionally engageratchet wheels I69 and place sufllcient drag on the spool from which theribbon is being drawn to insure tight winding of the ribbon on the otherspool.

Referring particularly to Fig. 14 for a description of the operation ofthe ribbon feeding mechanism, it will be noted that pawl I96 has beenpulled into engagement with the left-hand ratchet wheel I 69 by theover-center device comprising the link 208 and spring 204. In thisposition the right-hand upwardly extending abutment I98 is somewhatnearer to the rear of the mechanism than is the left-hand abutment. Itwill also be noted that the spring I89 is in front of the pivot pin I13and urges the arm I84 of retaining pawl lever I16 into engagement withthe left-hand ratchet wheel I69. The operating lever I92 is periodicallyrotated clockwise by the operating bail 206 and in being so rotated, itmoves the ratchet feed pawl I96 rearwardly of the typing unit, and thepawl, being in engagement with the left-hand ratchet wheel I69, rotatesit counterclockwise. Upon restoration of the lever I92 to its unoperatedposition, the pawl I96 is brought into engagement with the next tooth ofthe ratchet wheel preparatory to the next ribbon feeding operation. Asthe ratchet wheel is rotated counterclockwise, the outer end of arm I84of retaining pawl lever I16 engages successive teeth and preventsclockwise rotation of the ratchet wheel and thus restrains the wall ofthe aperture without aflecting the position of the pawl arm.

The direction of feeding of the ribbon may be reversed by rocking thelever I14 from the posiratchet from rotating with the operating pawl I96as the latter returns to its unoperated position. Itmay be added that asthe feeding of the left-hand ratchet wheel I69 takes place, the pin 202carried by the feed pawl I96 moves within the diamond-shaped aperture inthe retaining pawl arm I84 adjacent to the left-hand forward tion shownin Fig. 14 which is the extreme clockwise position, to that shown inFig. 15 which is the extreme counterclockwise position by .either of twomethods described below. Such movement of the lever I14 will carry theouter end of the arm I19 thereof out of alignment with the left-handabutment I98 of pawl I98 and into alignment with the right-handabutment. This operation does not in itself transfer the feedingoperation from the left-hand ratchet I69 to the right-hand ratchet. Thetransfer of the feeding operation will occur, however, upon the nextoperation of the operating lever I92 by bail 206. When the lever I92 isso operated, the pawl I98 will begin to move in ratchet feedingdirection in the same path that it had been following previously, butbefore it reaches the limit of its travel, the right-hand abutment I98will be blocked by the widened end I8I of the arm I19 of lever I14, andfurther movement of the feed pawl will cause it to be rotated about itspivot pin I94 in a clockwise direction and into engagement with theright-hand ratchet I69 with the assistance of the over-center link 209and spring 204. The bell crank lever I16 will be rocked simultaneouslyto its counterclockwise position due to the fact that the pin 202 isdisposed within the diamondshaped aperture I81 and will rock the leverI16 counterclockwise as the pawl I96 is shifted. The counterclockwiserotation of the bell crank lever I16 causes its over-center spring I89to shift to the rear of the pivot pin I13.

The feeding of the ribbonin opposite directions may becontrolledby'manual shifting of the lever I14 if desired, but theapparatus is intended for automatic reversal of the ribbon feed bycooperation of a portion of the ribbon itself with the perpendiculararms I18 of the lever I14. Ink ribbons of the kind used in typewritersare provided near their opposite ends with small metal eyelets or otherobstructions which are much wider than the thickness of the ribbons. Thebifurcations in the arms I18 are too narrow to permit these eyelets orother obstructions to pass. a ribbon is nearly reached and one of theobstructions engages an arm I18 of the lever I14, the latter is rotateddue to movement of the ribbon, and as soon as the lever has been rockedby thevmoving ribbon a distance sufilcient to block one of the abutmentsI98 of the pawl I96, the ratchet feeding will be transferred upon thenext operation of the operating lever in the manner described in theforegoing paragraph. It will be noted that due to the previouslydescribed dragging action of the leaf spring 201, which causes tightwinding of the ribbon, there is no slack to be taken up when theobstruction in the ribbon encounters the perpendicular arm I18 andplaces the additional load of the lever I11 on the ribbon. The ribbonwill thus continue to move and to be wound until the lever I11 has beenshifted and the direction of feeding reversed. With this arrangement,the moving ribbon is not required to effect the actual shifting of thefeed pawl from one ratchet to another against the resistance of itsover-center device but merely conditions ashift controlling lever whichconditions the pawl to be shifted by the power operated actuating leverupon the next operation thereof.

As a result, when the end of Operating cams' I62 is effected byoperating cams mounted the shaft 39 above the gear 4! (Fig. 4). The' eoperating cams are assembled in fixed relation with respect to eachother on a sleeve which is mounted on shaft -39 and which has associatedtherewith the driven portion of a spring loaded tooth clutch 2, thedriving portion of which is keyed or staked to shaft 39. A clutchthrowout lever 2I2 pivotally mounted on shaft 2I3 is spring biased intoengagement with the driven portion of the clutch 2!! and has an arm 214(Fig. 2) disposed in the path of a cam projection 2!. (Figs. 1 and 6)included on the selector cam barrel 62. With this arrangement, at agiven point in the cycle of operation of the cam barrel '62, camprojection 2!!! rocks the arm 2 which withdraws the clutch throw-outlever 2I2 from restraining engagement with the driven portion of theclutch 2!! and permits driving engagement to be established between theshaft 39 and the cams mounted thereon.

The uppermost of the cams is a channel or box cam designated by thereference numeral 2! 6, the cam groove 2!! (Fig. 9) of which receivesthe follower roller 2!!! rotatably mounted on a bell crank lever 2I9rockably mounted on the pivot shaft 22!. The bell crank lever 2 I 9 isarticulated at 222 to a bar 223 to which it is arranged to impart areciprocatory motion due to the fact that the cam groove 2!! has oneoffset 224 which,

when encountered by the follower roll 2I8, causes the lever 2| 9 to rockcounterclockwise upon its I mounting shaft 22! and in this way the bar223 is reciprocated rearwardly of the typing unit. A lever 226 is alsorockably mounted upon the shaft 22! and is secured at its forward end tothe cam operated bell crank 2I9 by a clamping bolt 22! which passesthrough a slot 228 in the bell crank 2I9. The slot 228 providesadjustability in the clamping together of the levers 2I9 and 226. Thelever 226 is effective in the conditioning of functions when they areselected, and its operation will be described later.

The bar 223 carries intermediate its ends an eccentrically mountedabutment 23!! against which abuts the operating arm 229 of a strikermember or hammer 23! pivotally mounted at 232 (Fig. l). 'The bar 223 hasa depending lug 220, and a tension spring 225 has one end connected tothe lug 220 and the other end connected to the operating arm 229 ofstriker 23!. The striker member 23! is provided at its upper end with amassive head 233 which describes an are as the hammer 23! is rocked andwhich delivers a sharp blow to an impact receiving abutment I39 ofresilient material, such as rubber or leather, carried by the printhammer operating lever arm !I'!. As indicated in Fig. 9, the offset 224in the groove 2!! of cam 2l6 is very abrupt and very short, so that thereciprocation of bar 223 to its rearmost position is very rapid and thusthe blow imparted by the striker member 23! to the print hammeroperating lever arm II! is very sharp. The bar 223 has a furtherfunction which it performs only under certain circumstances which willbe described later.

The cam which is directly beneath the cam 2I6 is designated by thereference numeral Ill! (Fig. 11) and hasv been described previously asthe operating cam for the transfer bail I02. No

- rocatory,

further description of this cam' is considered necessary.

The final cam in the group is disposed below the earn II! and isdesignated by the reference numeral 24!. This cam, as shown in Fig. 10,is

contoured to impart gradual rotation to a lever 242 pivoted on the stud22!. The lever 242 has a follower roll 243 which rides against the cam24!. As shown in Fig. 10, the radius of the cam 24! increases steadilyfrom minimum to maximum with an abrupt 'drop between the portions ofmaximum and minimum radius, and this causes the lever 242 which ispivoted on the shaft 244, to rotate counterclockwise steadily until itreaches its extreme counterclockwise position, whereupon it is restoredrapidly to its extreme clockwise position. A bell crank lever whichcomprises a single arm 248 and two arms 249 disposed in spacedhorizontal planes and in substantially the same vertical plane isadjustably connected to lever 242 by a clamping engagement afforded byscrew 24! extending through slot 246 in arm 249. Near their outer endsthe arms 249 support the pivot pin 25!. The pivot pin 25! serves asmeans for articulating to the bell crank lever arms 249 a spacing pawland a plurality of function performing bars. Cam 24! and levers 242and249 serve, through the elements articulated to the latter, as the meansfor effecting character spacing and function performance.

through the cooperation of elements provided therefor.

Spacing mechanism The spacing pawl designated by the reference numeral256 is articulated to the pin 25! through a spring yield connectioncomprising slot 251, spring 258, and guide pin 259 (Fig. 9). The pivotpin 25! enters the slot 25! and is urged to the forward end of the slotby the compression spring 258. The pin 259 is retained within the slotinside the convolutions of the spring 258 and prevents the spring fromescaping from the slot. The normal movement of the pawl 256 is recipdueto the rocking of the bell crank lever arm 249 by the cam 24!, but ifthe movement of the pawl 256 is blocked as it may be under certaincircumstances, the pin 25! may move within the slot and the spring 258will take up the movement imparted by the cam and will restore the pivotpin 25! to the forward end of the slot 25! when the cam follower 243 hasescaped from the highest portion of cam 24!. The pawl 256 has at itsopposite end a ratchet engaging prong. 26! which engages a ratchet 262to impart counterclockwise rotation thereto as the pawl is reciprocated.The pawl is spring biased into contact with the ratchet by a spring 263.The ratchet 262 is fixed to a rotatable carriage spacing shaft 264 whichcarries at its upper end a pinion 266 (Fig. 4) meshing with a rack 26'!connected to the platen carriage I4I. A stepby-step movement of thecarriage for letter spacing is effected by counterclockwise rotation ofthe spacing ratchet 262 responding to the reciprocation of the spacingpawl 256. As the carriage.

is stepped, it rotates the return spring drum I52 counterclockwise bydrawing the belt I5! left- Function mechanism The functions of thehereindescribed printing apparatus, such as Line feed, Shift, Unshifetc., are selected in accordance with stop positions of the type wheel,as determined by certain of the stop pins 96 which may be selected bythe code discs'91, are conditions for operation by the lever 226actuated by the print hammer operating cam 2.16, and are performed bythe lever arms 249 actuated by the spacing cam 241. Any other desiredfunctions may be selected, conditioned, and operated in the same manner,and in the present embodiment of the invention, certain other ones areso controlled, these functions providing for the operation of electricalcontacts for circuit control, such as rendering the:

transmitting mechanism inoperative, remotely controlling apparatus forstopping the operating motor, and operating an audible signal, such as abell.

Other functions, particularly those which may conveniently be performedwith great rapidity, may be actuated directly from the print hammeroperating cam 216, rather than from the less violent spacing cam 241. Inthe present embodiment of the invention "Carriage return and "Spacesuppression" are so controlled.

Since, as hereinbefore outlined, the selection of functions iscontrolled in accordance with certain stop positions of the type wheel,means must be provided for effecting response of the functionconditioning or performing mechanisms. Such means has been provided onthe type wheel shaft 44 just above the gear 43 and comprises a pluralityof index pins or abutment pins 211 (Figs. 9 and 12) disposed in varioushorizontal planes and in various radial positions with respect to thetype wheel. In certain horizontal planes, only one index pin is found,whereas others contain several pins. The number of pins in a horizontalplane indicates the number of type wheel stop positions in which aparticular function is selected. Index pins in different horizontalplanes may be disposed in the same vertical plane, indicating that aplurality of functions may be selected simultaneouslyJ For cooperationwith the index pins 211 there are provided a plurality of superposedlevers, the uppermost of which is designated 215 in Figs. 9 and 12,pivotally mounted at their forward ends on a pivot pin 210 carried atthe rearmost end of lever 225 and extending through and supported inhorizontal slots in a plate 213. The levers are aligned with the indexpins 211 in the several horizontal planes, and each carries an abutmentarm 212 extending leftwardly therefrom at a point on the lever towardwhich the associated type wheel shaft index pin 211 points when theshaft is stopped in the position to select the function represented bythat pin. At their rearmost ends the lever 215 and corresponding leversare provided with disc-like portions 214 disposed in notches in theforward ends of associated function levels which are pivotally mountedon the pivot shaft 216 and which will be identified by individualreference numerals in the description of the several functionoperations,

Since the lever 215 and corresponding levers are articulated to thelever 226 (Fig. 9), they undergo movement when the print cam 216operates lever 226, and a lever such as 215 associated with selectedindex pin 211 moves differently than do those associated with unselectedindex pins. The function levers to which the lever 215 and correspondinglevers are articulated by their disc-like portions 214 are biased totheir unoperated positions by springs 211, and they rotate in oppositionto the tension of such springs only when forced to do so. .When thelever 226 is actuated by cam 216, it carries the pivot pin 219leftwardly as viewed in Fig. 9, and with it the forward ends of lever215 and those disposed below it. If no index pins 211 are aligned withthe abutment arms 212, the lever 215 and corresponding levers pivotabout their disc-like portions214 and rock idly. If, on the contrary, anindex pin is aligned with an abutment arm 212, it blocks the leftwardmovement of that arm, and becomes a fulcrum for the particular lever,thus causing the lever to operate as a first class lever to actuate itsassociated function lever and rotate the latter counterclockwise.

Certain of the function levers operated by the lever 215 andcorresponding levers are adapted to perform the associated function andothers are adapted to condition a function. The conditioning is effectedthrough superposed function performing bars, the uppermost of which isdesignated 289, pivotally mounted on the pivot pin 251 carried by thespacing cam operated bell crank leverarms 249. The function bar 280 andcorresponding bars are supported intermediate their, ends in spacedhorizontal slots 219 in the vertical plate 213 (Fig. 1). They arereciprocated rearwardly when the bell crank lever arms 249 are rotatedcounterclockwise by cam 241 and they may rotate about the pivot pin 251within the confines of their supporting slots 219. They are biasedcounterclockwise by springs 219.

Fig. 12 displays an exploded perspective view of the functionconditioning and performing levers and also shows the relative angularpositions of the index pins 211 when the lowermost pin is selected. Themechanism for performing the several functions will be described, andreference will be made to other figures in which parts of the functionperforming mechanisms are shown.

Carriage return The uppermost index pin 211 and lever 215 are associatedwith the restoration of the platen carriage 141 to line beginningposition, which is accomplished by withdrawing the spacing pawl 256 andretaining pawl 261 (Fig. 9) from engagement with the feed ratchet 262,whereupon the spring loaded drum 152 acts through the belt 151 torestore the carriage to its extreme righthand position. The functionlever to which the lever 215 is articulated is designated 281, and thislever is rotated counterclockwise when the uppermost index pin 211 iseffective upon its associated lever 215. The lever 281 carriesupstanding pins 282 and 283 located at the left and right of the spacingpawl 256 and the retaining pawl 265, respectively, and in close.proximity thereto. When the lever 281 is rotated counterclockwise, itmoves the pins 282 and 28.3 to right and left, respectively, and thepins rotate the spacing pawl 259 and retaining pawl 265 clockwise abouttheir pivotal mountings 251 and 268, respectively, to withdraw the pawlsfrom engagement with the ratchet 262. The carriage, being under no otherrestraint, responds to the force exerted by the spring in the drum 152and moves to its extreme righthand position, rotating the spacingratchet 262 clockwise as it does so.

It will be noted that the lever 28I' is provided, near its rearmost end,with a notch in which are formed shoulders 289 and 281 (Fig. 12). Alatching lever 28! is pivotally mounted at 288 and is biased forclockwise rotation by spring 28I which has one end connected to thelever 288 and the other end connected to the function lever 28I. Whenthe function lever 28I is in its unoperated or extreme clockwiseposition as viewed in Figs. 9 and 12, the lever 288 is held inengagement with the shoulder 286 by spring 29I. The rocking of thefunction lever 29I counterclockwise to effect a carriage returnoperation permits the lever 289 to escape from the shoulder 286 and tocome to rest against the shoulder 281 whereby the function lever 28l islatched in its operated position to maintain the pawls 266 and 265 outof engagement with the ratchet 262. The purpose of latching the functionlever 28I in the operated position is to permit the carriage I4I.whichmay bounce slightly as it comes into engagement with the dashpotcontrolled lever I56 or the stop screw I64, to settle into its extremeright-hand position before the pawls are permitted to reengage thespacing ratchet 262. Manifestly, the function lever 28I must beunlatched before any carriage spacing operation can occur and anarrangement has been provided whereby the lever 28I' is uniatched uponthe next operation of the cam M6.

The arrangement includes a lever 292 (Fig. 9) which has a slot 293 whichis entered by a screw 294 carried by lever 288. The slotted engagementbetween lever 288 and lever 292 provides a yielding connection, and aspring 296, which has one end connected to the lever 292 and the otherend connected to an extension of the lever 288, tends to rotate thelever 292 in a counterclockwise direction which is prevented by a lug2'91 carried by a fixed plate 295 against which the lever 292 rests.Since the spring 296 is disposed between the lug 291 and the screw 294,the extreme left end of the slot 293 abuts against screw 294. A rod 298is slidably supported in the lug 291 and'in a portion 299 of the frameof the mechanism and occupies the same horizontal plane as the lever292. The rod 298 slides freely within frame .memher 299 and the mg 291and is urged to its rightward position by the lever 292. The lever I56which is articulated to the dashpot plunger rod I58 carries aneccentrically mounted adjustable abutment 39I in alignment with theright-hand end of the rod 298. The abutment 39I is similar to thepreviously described abutment 239 and is below the pivotal mounting I51of the lever I56 so that it is moved toward the rod 298 as the carriageI 4| rotates the lever I56 clockwise at the completion of a carriagereturn operation. When the lever I56 comes to rest in its extremeclockwise position at the conclusion of the carriage return operation,its abutment 39I moves the rod 298 leftwardly a distance sllfilcient tocause it to rotate the lever 292 clockwise and position the forward endof that lever in alignment with the rod 223 articulated to the bellcrank lever 2I9. Lever 292 will occupy this position as long as thecarriage MI is in its extreme right-hand position and upon the nextcounterclockwise rocking of the bell crank lever 2I9 by the box cam 2I6,rod 223 will be reciprocated rearwardly and will communicate itsreciprocating motion to lever 292, which will cause the latching lever288 to be rotated counterclockwise out of engagement with the shoulder281 and into engagement with the shoulder 266. The function lever 28Iwill thus be restored to its unoperated positon and the pawls 269 and281 will reengage the spacing ratchet 292 in preparation for normalspacing operations. The slotted mounting of lever 292 provides a yieldconnection which may, under certain circumstances, operate yieldingly onaccount of a blocking condition. The carriage I may, particularly if ittravels through only a short distance in returning to its extremeright-hand position. reach that position while the bar 223 (Fig. 9) isbeing operated by the cam 2 and before the bar has been withdrawn to itsforemost position. Under this condition the rod 298 might jam theforward end of lever 292 against the right-hand face of operating bar223, whereby the rod 298 might be prevented from traveling its normaldistance and the carriage I be prevented from assuming its extremeright-hand position. The slotted connection permits the lever 292 to befully moved by the rod 298, even should the forward end of lever 292 beblocked by bar 222.

Shift and unshijt mechanisms It will be convenient to postpone thedescription of the functions associated with the multiple sets of indexpins occupying the second and third positions from the top on the typewheel shaft 44 until the remaining functions have been described, thereason for such postponement being that the description of the functionsthus passed over will be more readily understandable. Accordingly,attention is directed to the function lever 892 (Fig. 12) carried by theshaft 216 in alignment with and articulated to the lever 395, which isassociated with the index pin in the fourth level from the top. Thefunction lever 392 is associated with the shift operation by means ofwhich the type wheel is shifted to remove one of the annular sets oftype pallets from alignment with the print hammer I36 and to bring theother set of type pallets into alignment therewith. The lever 392 doesnot perform the shift function but merely establishes a condition as aresult of which the function may be performed, and to this end it isprovided with a projection 893 which occupies the same horizontal planeas the bar 289. This bar has its rearmost end disposed slightly to theleft of a latching projection 394 of a latching lever 396 which ispivotally mounted on shaft 268 (Fig. 9) and is biased in a clockwisedirection by spring 3I9. All levers corresponding to lever 396 arebiased clockwise by springs 3I9 and are limited by abutment against stud399 (Fig. 9). Upon the selection of the index pin associated with thelever 395, and upon the operation of that lever, the

lever 392 is rotated counterclockwise similarly to the previouslydescribed function lever 28I, and

through its projection 393 it imparts a clockwise rotation to the bar289. The latter bar, in rotating, moves to the right of latchingprojection 394, and at the same time it moves rearwardly due tooperation of bell crank lever'arms 249 by cam 2 I6, and becomes latchedin its clockwise position.

The bar 289 carries on the right side thereof a projection 391 which isdisposed. in alignment with the lower end of a shifter lever arm 398(Figs. 7 and 8) to which it imparts a counterclockwise motion as viewedin Fig. 7 as the bar 289 is reciprocated rightwardly due to continuedcounterclockwise rocking of the bell crank lever arms 249 by the cam I.The shifter lever arm 398 is one arm of a bell crank lever pivotallymounted upon the previously described pivot shaft 282 and having itsother arm 3 extending rearwardly of the printer. The lever arm 3 is bi-'furcated at its outer end and has disposed in the bifurcation a pin 3 I2 carried by arm 3I3 of shifter frame 3. The frame 3 is mounted on shaft232 by means of slot 3I3 so that it may be raised and lowered verticallyto lift and lower the typ wheel through its horizontal arm 3" (Figs. 1and 4), which is guided on guide screw 3i! and which engages the typewheel hub I23. The operation of the lever arm 308 upon the shifter frame3 I4 is to lift the latter through the articulation of the lever arm 3to the frame 3 by virtue of the pin 3I2. The frame 3 carries a pivotedspring loaded detent 3I0 which has notches at the lower end thereof,either of which may en-. gage a bushing 3l3 on the shaft 232 to maintainthe shifter frame 3I4 in a position to which it is moved. A spring 3I4'(Fig. l) counterbalances the shifter frame 3 and type wheel MI, and thusequalizes the forces required to effect shift and unshift operations.

Referring again to Fig. 12, it will be observed that a function lever32I similar to the lever 302 and having a projection 322 is pivotallymounted on the shaft 216 below the lever 302 and in articulation withthelever 326. Two angularly spaced index pins 2" are disposed in thesame horizontal plane as the levers 32I and 326, which indicates thatthere are two stop positions of the type wheel shaft which will resultin operation of the function lever 32I. Lever 32I is associated with theunshift function of the printer. An operating bar 320 is aligned withthe function lever projection 322 and is also aligned with a latchinglever 323 below and similar to the latching lever 306 and provided witha latching projection 324. The operating bar 320 is articulated to thepivot pin 25I directly below the operating rod 280 and is provided atthe side thereof with a projection 326 (Fig. '7) which, when the rod islatched in its extreme clockwise position by the projection 324 of lever323, is disposed in operating alignment with a lever arm 321 similar tothe lever arm 308 but necessarily slightly longer than that lever arm.The lever arm 321 constitutes, together with a forwardly extending arm328, a bell crank lever pivotally mounted upon the pivot shaft 232. Theouter end of the lever arm 328 is bifurcated similarly to the lever arm3 and engages a pin 323 carried by a forwardly extending arm 33I of theshifter frame 3. When the lever arm 321 is rocked in counterclockwisedirection due to movement of the projection 326 of the operating bar320, the lever arm 328 will also be rocked counterclockwise and willmove pin 323 downwardly, whereby shifter frame 3I4 is moved downwardlyto effect an unshift operation. It is apparent that the lever arms 306and 321 operate oppositely and simultaneously so that as one efiectsmovement of the shifter frame, the other is oppositely rotated andpresented in'position to be next effective in the shifting of theshifter frame 3.

It was previously mentioned that the unshifting operation conditioned bythe function lever 32I and performed by the bar 320 may be selected foreither of two stop positions of the type wheel shaft, as indicated bythe presence of two index pins 2" in the same horizontal plane, eitherof which may be effective. One of the pins is associated with theunshift signal and is presented in operating position when the signalcombination assigned to unshifting is received. The other pin ispresented in operative position when that code combination is receivedwhich is assigned to spacing, for the reason that it has been found thatin many instances printing following a blank spacing operation is to beeffected with an unshift condition of the printing mechanism, and it istherefore convenient to effect the unshifting automaticallysimultaneously with the spacing, thus obviating the transmission of aseparate unshift code combination.

Line feed The single index pin immediately below those assigned to theunshift function is associated with the line feed function which is afunction accomplished by rotating the printing platen I33 to advance asheet or web of paper upon which printing is to be effected through adistance sufllcient to present a line of blank paper to the printingposition. The selection of the line feed Index pin and the rocking ofthe lever 335 (Fig. 12) against the pin causes the operation of afunction lever 332 which is similar to the levers 302 and 32I and whichhas a projection 333 for operating the associated function performingbar 340. A function operating lever 334 i pivotally mounted below thelatch lever 323 on the pivot shaft 268 and is similar to that leverexcept that it has operative connection with the line feeding mechanism,as will be described, and is therefore a true function performing lever,and it has no latching projection. A separate latching lever 336 isprovided which is also pivotally mounted on the pivot shaft 268 andwhich has at its righthand end a forwardly projecting arm 331 whichterminates in an upwardly turned projection 338 which occupies aposition with respect to the lever 334 corresponding to the latchingprojections 304 and 324 of levers 306 and 323, respectively. The lever336 is spring biased in a clockwise direction by spring 333, movement inthat direction being limited by the stud 300 (Fig. 9), and it is capableof counterclockwise rotation independentl y of the lever 334 to permitit to be cammed in a counterclockwise direction by the operating bar 340and to return to its extreme clockwise po sition where its latchingprojection 338 latches the operating bar 340 in conditioned position.When the function bar thus latched is reciprocated rearwardly in themanner common to all of the function performing bars, the lever 334 isrotated counterclockwise about the pivot 268. The lever 334 has securedthereto at its righthand end by screw 34I a link 342 which is providedwith a slot in which is disposed the operating arm 343 of a line feedbail 344, The bail 344 (Figs. 4 and 21) is pivotally mounted in suitablebrackets 346 on the rear of the machine and extends slightly above thelower end of the previously described line feeding lever I60. The leverI60 travels with the carriage MI and the extent of the bail 344transversely of the machine is slightly greater than the travel of thelever I60, so that the lever may be engaged by the bail at any positionin the travel of the carriage. The line feed lever I60 is provided withan anti-friction roll I48 which constitutes means for engagement of thebail 344 with the lever I60. A certain amount of freedom is provided inthe interconnection between the link 342 (Fig. 12) and the lever 334 topermit the link to rock with respect to the lever. The slot into whichthe arm 343 of the bail 344 enters also provides limited freedomnecessitated by the rocking movement of the arm 343 within thereciprocated link 342. A tension spring 341 keeps the arm 343 fromchattering within the slot in the link 342.

